US6463847B1 - Hoop-casing device - Google Patents

Hoop-casing device Download PDF

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Publication number
US6463847B1
US6463847B1 US09/463,288 US46328800A US6463847B1 US 6463847 B1 US6463847 B1 US 6463847B1 US 46328800 A US46328800 A US 46328800A US 6463847 B1 US6463847 B1 US 6463847B1
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cam
rotation axis
control shaft
rotation
cams
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Expired - Fee Related
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US09/463,288
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English (en)
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Manfred Rauch
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Fromm Holding AG
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Fromm Holding AG
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65B—MACHINES, APPARATUS OR DEVICES FOR, OR METHODS OF, PACKAGING ARTICLES OR MATERIALS; UNPACKING
    • B65B13/00—Bundling articles
    • B65B13/18—Details of, or auxiliary devices used in, bundling machines or bundling tools
    • B65B13/24—Securing ends of binding material
    • B65B13/32—Securing ends of binding material by welding, soldering, or heat-sealing; by applying adhesive
    • B65B13/327—Hand tools

Definitions

  • This invention concerns a device for hooping an object by means of a heat-weldable plastic strip strapped around it.
  • a hoop-casing device of the aforementioned type is known for instance from U.S. Pat. No. 3,269,300 and comprises a means for tensioning the strip and a means for friction-welding two mutually overlapping strip portions of the tensioned strip between two welding jaws.
  • Each of these means is assigned a motor, a switch for controlling this motor via a control circuit, and a cam for actuating the switch.
  • the two cams can be rotated jointly about a common rotation axis.
  • One of the welding jaws can be displaced in a direction essentially orthogonal to the rotation axis while being adjustable by means of a cam gear.
  • the cam gear comprises a cam disk that can be rotated about the rotation axis along with one of the cams, and a telescopic tappet that is functionally arranged between the cam disk and the displaceable welding jaw and is telescopically retractable or extensible in a direction essentially othogonal to the rotation axis and is spring-loaded loaded in its direction of extension.
  • a drawback of this known hoop-casting device is that the force that presses the welding jaws against the plastic strips depends on the latter's thickness. If the pressing force is too great the motors are demanded too much power output, the rotation speed of the motors drops, and the hoop-casing device no longer operates properly. Nevertheless, in this known hoop-casing device there is provided no adaptation capability that would allow to use plastic strips of various thickness values.
  • the object of the invention is to provide a hoop-casing device of the relevant generic type that does not have the aforementioned drawback and hence, that will allow for the use of plastic strips of various thickness values.
  • the maximum force that urges the welding jaws towards each other is determined by the rotational position of the cam disk relative to at least one of the cams, all the more as this maximum force appears at an extremal rotational or angular position of the cam disk that results from at least one of the cams having a restricted rotation capability in the course of its rotation about the rotation axis relative to the device.
  • the invention allows this maximum force to be adjusted by means of the adjustment of the rotational position of the cam disk relative to said cam and thus, to be selected depending on the thickness of the plastic strips, which allows to use the hoop-casing device with plastic strips of various thickness values.
  • plastic strips of 0.4 mm to 1.05 mm thickness can be used, with the force that presses the welding jaws onto the plastic strips being adjustable so as to keep almost the same value, so that the hoop-casing device always operates properly independent from the thickness of the plastic strips.
  • one of the cams can be assigned a stop projection to limit its rotation about the rotation axis in cooperation with a stop fixedly arranged at the device, which will determine the extremal rotational or angular position of the cam disk that, for its part, will determine the maximum force that urges the welding jaws towards each other.
  • the cams each are arranged at a respective assigned shaft part.
  • the rotation axis is shared between both shaft parts.
  • the two shaft parts can be separated from each other between the two cams or connected to each other rigidly with regard to rotation in respect of each other by means of a mutually meshing gear.
  • This gear is embodied as a longitudinal gear having generatrices oriented parallel to the rotation axis.
  • one of the two shaft parts is embodied as a trunnion and provided with an external toothing and the other one is embodied as a sleeve part provided with an internal toothing.
  • the two shaft parts can be coaxially inserted into, displaced relative to, and separated from, each other.
  • the cam disk embodied as an eccentric cylinder is arranged at a shaft part that is rotatable relative to, and fixed in axial direction relative to, the device, whereas the other shaft part is arranged at the device so as to be rotatable as well as displaceable in axial direction.
  • the shaft part that is displaceable in axial direction is supported by means of a spring element at a housing portion that is fixedly arranged at the device, arranged to protrude from the housing portion, and stressed by the spring element towards the shaft part that is fixed in axial direction.
  • the shaft part that is displaceable in axial direction can be pulled out manually at the housing portion—with the help of a knob provided for this purpose—and then angularly displaced, upon its release the pulled-out shaft part will tend to mesh again with the other shaft part: the relative rotational position of the shaft parts thus arrived at will determine the relative rotational position of the stop projection and the cam disk and hence, the extremal rotational or angular position of the cam disk and the maximum force that urges the welding jaws towards each other, in this manner this urging force can be adjusted to fit the thickness of the plastic strips.
  • the one longitudinal toothing is provided with a bridgework region in which a plurality of teeth appear to be fused together from tip to tip when viewed in cross-section, this one longitudinal toothing thus being provided with a filling.
  • the other longitudinal toothing is provided with a teeth gap region in which a plurality of teeth have been omitted from root to root when viewed in cross-sectional, this other longitudinal toothing thus being provided with a recess.
  • the bridgework region extends across a smaller number of teeth and thus, with respect to the rotation axis, across a circular arc of smaller extent than the teeth gap region. In this manner the two shaft parts may only be connected i.e. mesh one into the other over a predetermined sensible region, whereas unreasonable and hazardous operating conditions are avoided.
  • FIG. 1 shows a perspective explosion view of parts of the hoop-casing device in order to illustrate the hoop-casing device according to the invention in an end position thereof;
  • FIG. 2 shows a further perspective explosion view of the parts of the hoop-casing device according to FIG. 1, represented in another viewing direction;
  • FIG. 3 shows a perspective view of the parts of the hoop-casing device according to FIG. 1 mounted at each other;
  • FIG. 4 shows a perspective explosion view of two particular parts of the hoop-casing device according to FIG. 1 in order to illustrate a mutual longitudinal toothing of these parts;
  • FIG. 5 shows a perspective explosion view of parts of a hoop-casing device in order to illustrate the hoop-casing device according to the invention in a particular initial position thereof;
  • FIG. 6 shows a further perspective explosion view of the parts of the hoop-casing device according to FIG. 5, represented in another viewing direction;
  • FIG. 7 shows a perspective view of the parts of the hoop-casing device according to FIG. 5 mounted at each other;
  • FIG. 8 shows a perspective explosion view of parts of a hoop-casing device as in FIG. 5, however, with the hoop-casing device according to the invention in another initial position;
  • FIG. 9 shows a further perspective explosion view of the parts of the hoop-casing device according to FIG. 8, represented in another viewing direction;
  • FIG. 10 shows a perspective view of the parts of the hoop-casing device according to FIG. 8 mounted at each other;
  • FIG. 11 shows a side view of parts of a hoop-casing device in the same initial position as in FIGS. 5, 6 and 7 in order to particularly illustrate the cams and switches and their cooperation;
  • FIG. 12 shows a side view of parts of a hoop-casing device in the same initial position as in FIGS. 8, 9 and 10 in order to particularly illustrate the cams and switches and switches and their cooperation;
  • FIG. 13 shows a side view of the shafts according to the invention of a hoop-casing device in the same end position of the shafts as in FIGS. 1, 2 and 3 , as well as a sectional view of housing portions of the hoop-casing device passing through a rotation axis of the shafts and a direction of displacement of welding jaws of the hoop-casing device;
  • FIG. 14 shows a perspective view of the parts of the hoop-casing device according to FIG. 1 mounted at each other, however, with the hoop-casing device according to the invention in another end position.
  • a hoop-casing device of the relevant generic type serves to hoop an object with a heat-weldable plastic strip placed around it, with a loop being made around the object from this strip and then tensioned. Once the strip has reached an appropriate tension it is sealed to form a hoop by heat-welding overlapping ends thereof.
  • the hoop-casing device according to the invention will be described below with reference to an exemplary embodiment that is deemed particularly advantageous, it being understood that the invention must not be limited to this exemplary embodiment.
  • the hoop-casing device is provided with a unit, driven by a tensioning motor, for tensioning the plastic strip.
  • a tensioning motor for tensioning the plastic strip.
  • Such a unit is well known per se, for instance from the aforementioned document U.S. Pat. No. 3,269,300, and will not be described here in detail because it is the control of the motor of this unit that matters in the embodiment of the hoop-casing device described here.
  • the hoop-casing device is provided with a unit for friction-welding two mutually overlapping strip portions of the tensioned strip between two welding jaws driven by a friction-welding motor.
  • the principle of such a unit is known per se, for instance from the aforementioned document U.S. Pat. No. 3,269,300.
  • FIG. 2 there are shown the tensioned plastic strip 1 and the welding jaws 2 and 3 that grip it (FIGS. 2, 6 , 9 , 13 ).
  • FIG. 2 there are shown the tensioned plastic strip 1 and the welding jaws 2 and 3 that grip it (FIGS. 2, 6 , 9 , 13 ).
  • the shaft 51 of the friction-welding motor is visible in a sectional view, which shaft reciprocates the welding jaw 2 during the friction-welding operation via an eccentric bearing 52 and a connecting rod 53 relative to the other welding jaw 3 that is fixedly arranged at a housing portion 54 of the hoop-casing device.
  • the two aforementioned motors are controlled by a switch assigned thereto via an control circuit assigned thereto.
  • Such motors can be embodied as electric motors, but also as pneumatic motors, and can be assigned an electric, electro-pneumatic or pneumatic control ciruit, as may be the case.
  • pneumatic motors can be assigned an electric, electro-pneumatic or pneumatic control ciruit, as may be the case.
  • a control block 55 (FIG. 13) is arranged at a housing portion 54 of the hoop-casing device and accommodates the two switches and electronic control circuits for the motors (in FIGS. 4 and 13 the two switches 4 and 5 are not visible, in FIGS. 11 and 12 the two switches are positioned exactly one behind the other, the switch 4 conceals the switch 5 ).
  • the switches 4 and 5 each are provided with a switch lever 24 and 25 , respectively, that, for its part, is provided with a pickup roller 34 or 35 , respectively (indicated in FIGS. 6, 7 , 11 , 12 ) by means of which the switches 4 and 5 each are controlled by a respective cam 6 or 7 assigned thereto.
  • the two cams 6 and 7 can rotate independent from each other about a common rotation axis 8 , and they can cooperate by having a stop projection 26 of the cam 6 (indicated in FIGS. 1, 2 , 3 , 4 , 11 , 12 , 14 ) meeting a stop 27 (indicated in FIGS. 1, 2 , 3 , 7 , 11 , 12 , 14 ).
  • the tensioning motor is controlled by the cam 7 that is mounted at a sleeve part 9 (FIGS. 1, 3 , 10 , 13 ) of the housing portion 54 and can rotate about the rotation axis 8 .
  • the cam 7 is provided with an actuation lever 57 whose root portion 62 (FIG. 2) acting as a stop projection can meet a stop 63 (FIG. 1) of the housing portion 54 , which will limit the rotation of the cam 7 .
  • the actuation lever 57 is stressed towards the stop 63 by a spring 65 (FIGS. 1, 5 , 8 ) that passes through a guide tube 64 .
  • a control shaft 10 is supported at the housing portion 54 , coaxial to the sleeve part 9 , and can rotate about the rotation axis 8 .
  • An actuation lever 16 is provided at the one end of the control shaft 10 .
  • the latter is provided with a toothing 12 that fits releasably to a toothing 36 (FIGS.
  • the above-described position of the cams 6 and 7 is an end position (FIG. 3 in a perspective view, FIGS. 1 and 2 in an explosive view).
  • the corresponding end position of the control shaft 10 having arranged at it the actuation lever 16 depends on the relative rotational position in which the cam 6 is mounted at the control shaft 10 .
  • the use of a different relative rotational positionwhen the cam 6 is being mounted at the control shaft 10 will result in an different end position of the control shaft 10 and the actuation lever 16 (FIG. 14 ).
  • the thus attained end position of the control shaft 10 i.e. its extremal rotational or angular position determines the force with which the welding jaws are urged towards each other.
  • the welding jaw 2 (i.e. that one of the two welding jaws 2 and 3 which is located next to the control shaft 10 ) can be displaced relative to the housing portion 54 in a direction essentially orthogonal to the rotation axis 8 (FIG. 13 ).
  • the distance of the welding jaw 2 to the rotation axis 8 is determined by the position of the other welding jaw 3 and the thickness of the plastic strip 1 located inbetween.
  • the force with which the welding jaws 2 and 3 are urged towards each other and compress the plastic strip 1 can be adjusted by means of a cam gear 13 .
  • This cam gear 13 comprises, in the role of the cam disk 14 , an eccentric cylinder (more clearly visible in FIGS.
  • the retractable and extensible telescopic tappet 15 comprises two tappet parts 19 and 20 that can be telescopically displaced with respect to each other, and between them a compression spring element 21 that stresses the telescopic tappet 15 in a direction of extension thereof. Between the cam disk 14 and the tappet part 19 there is also arranged a sliding sleeve 22 .
  • a thrust part 23 and a ball or roller bearing 28 are arranged, adjacent to each other, a thrust part 23 and a ball or roller bearing 28 , whereby the force exerted by the compression springer 21 in a direction orthogonal to the rotation axis 8 is transferred by the tappet part 20 onto the thrust part 23 , and whereby balls or rollers of the bearing 28 pass this force further onto the welding jaw 2 .
  • the welding jaws 2 and 3 are urged onto each other and to compress the plastic strip 1 located inbetween, as may be the case.
  • the force with which the welding jaws 2 and 3 are urged towards each other and compress the plastic strip 1 is determined by the effective length of the telescopic tappet 15 , i.e. by the relative position of the tappet parts 19 and 20 , which position, for its part, depends on the rotational position of the cam disk 14 and consequently, on the rotational position of the control shaft 10 in the respective end positions.
  • a rotation of the control shaft 10 away from its end position first relieves the welding jaws 2 and 3 from being urged towards each other and eventually (in the course of further rotation) lifts off the weldings jaws 2 and 3 from each other.
  • the parts of the cam gear 13 are arranged (in a manner not shown) fixedly adjacent to each other in a direction essentially orthogonal to the rotation axis 8 , and the extension of the telescopic tappet 15 is limited (in a manner not shown) by a system of transversal pin and longitudinal slot, which allows the telescopic tappet 15 to lift off and pull away the welding jaw 2 from welding jaw at a corresponding rotational position of the control shaft 10 .
  • control shaft 10 can be rotated up to a starting position (FIGS. 5, 6 , 7 , 8 , 9 , 10 ) in which a stop projection 30 (FIGS. 5, 6 , 8 , 9 ) of the actuation lever 16 meets a stop 31 (FIGS. 6, 9 ) of the housing portion 54 .
  • a starting position FIGS. 5, 6 , 7 , 8 , 9 , 10
  • a stop projection 30 FIGS. 5, 6 , 8 , 9
  • stop 31 FIGS. 6, 9
  • a catch holds the actuation lever 16 in this starting position by providing resistance against unintentional rotational displacement: this catch is made up of a recess 37 of hollow-spherical shape provided in the actuation lever 16 (FIGS. 1, 5 , 8 ) in cooperation with a ball 38 (FIGS. 5, 6 , 8 , 9 ) that is stressed towards the recess 37 by a spring 39 , the spring 39 and at least part of the ball 38 being arranged in an accommodating bore hole 40 (FIGS. 2, 6 , 9 ) of the housing portion 54 .
  • the stop projection 26 of the cam 6 cooperates with the stop 27 of the cam 7 .
  • a rotational displacement of the actuation lever 57 brought about by the operator's thumb causes, by means of the stop 27 of the cam 7 and the stop projection 26 of the cam 6 , a rotation of the control shaft 10 away from its corresponding end position, which will relieve the welding jaws 2 and 3 from being urged towards each other and manifest itself in the rotational movement of the actuation lever 16 . In this manner it is ensured that no tensioning of the plastic strip 1 will be triggered unnoticed and unintentionally as long as the welding jaws 2 and 3 fail to be completely lifted off from each other.
  • the force with which the welding jaws 2 and 3 are urged towards each other and compress the plastic strip 1 during the welding process is determined by the rotational position of the control shaft 10 in the respective end positions (FIG. 3 or 14 , respectively). Due to the simultaneous cooperation of, on the one hand, the stop projection 26 of the cam 6 with the stop 27 of the cam 7 , on the other hand, the root portion 62 of the actuation lever 57 of the cam 7 with the stop 63 of the housing portion 54 , these end positions, for their part, depend on the rotational position of the cam 6 on the control shaft 10 .
  • the relative rotational position of the cam disk 14 and the cam 6 can be adjusted by means of the relative rotational position in which the cam 6 is mounted at the control shaft 10 , as described in the following.
  • Tile cam 6 is provided with a sleeve part 41 (FIGS. 5, 8 ) that is constructed on the inside to be provided with the toothing 36 and on the outside to be cylindrical.
  • a sleeve part 41 (FIGS. 5, 8 ) that is constructed on the inside to be provided with the toothing 36 and on the outside to be cylindrical.
  • By means of its cylindrical outside sleeve part 41 is arranged at the end of an auxiliary shaft 32 in a cylindrical accommodating sleeve 42 and attached thereto by means of an adapter sleeve 33 (FIGS. 4, 6 ).
  • the auxiliary shaft 32 is positioned coaxial to the control shaft 10 in the continuation thereof along the rotation axis 8 .
  • the auxiliary shaft 32 is supported in axially displaceable manner in a bearing 43 (FIG. 13) of a further housing portion 44 fixedly arranged at the housings portion 54 .
  • An end portion 46 of the auxiliary shaft 32 protrudes from the housing portion 44 and is provided with a knob 45 at its free end.
  • a spring 56 (FIG. 13) is arranged on the auxiliary shaft 32 between the accommodating sleeve 42 and the housing portion 44 and stresses the accommodating sleeve 42 towards the control shaft 10 .
  • a knob 45 provided at the free end of the auxiliary shaft 32 , the auxiliary shaft 32 can be pulled axially, away from the control shaft 10 , against the force of this spring 56 , which releases the mutual meshing of the toothing items 12 and 36 and at the same time pulls away and removes the cam 6 from the control shaft 10 .
  • the knob 45 is released the toothing items 12 and 36 again meet with each other and mesh as corresponds to the relative rotational position of the cam 6 and the end 11 of the control shaft 10 i.e.
  • the toothing 12 stops just short of the end 11 of the control shaft 10 and this end 11 , for its part, is embodied as a trunnion of smaller diameter.
  • the two cams 6 and 7 each are arranged at a respective assigned shaft part, namely the control shaft 10 and the auxiliary shaft 32 , respectively; these two shaft parts each are provided with a common rotation axis 8 and can be separated from each other or connected to each other rigidly with regard to rotation in respect of each other between the two cams 6 and 7 by means of a mutual meshing of toothing items.
  • the one shaft part, namely the control shaft 10 is arranged at the device so as to be rotatable and fixed in axial direction, and supports the cam disk 14 .
  • the other shaft part 32 is arranged at the device so as to be rotatable and diplaceable in axial direction, the axially displaceable shaft part 32 is supported by means of a spring element 56 at a housing portion 44 that is fixedly arranged at the housing portion 54 , it is arranged protruding from the housing portion 44 , and it is stressed by the spring element 56 towards the shaft part 10 that is fixed in axial direction.
  • the toothing items 12 and 36 are embodied as longitudinal toothing items having respective generatrices 49 and 50 oriented parallel to the rotation axis 8 (FIG. 4 ).
  • the longitudinal toothing 12 is an external toothing located in the vicinity of the trunnion-shaped end portion 11 of the control shaft 10 .
  • the longitudinal toothing 36 is an internal toothing located within the sleeve part 41 of the cam 6 that, for its part, is located within the accommodating sleeve 42 at the end of the auxiliary shaft 32 , so that the longitudinal toothing 36 is arranged in the vicinity of an end portion of the auxiliary shaft 32 .
  • the two longitudinal toothing items 12 and 36 can be coaxially inserted into, displaced relative to and separated from each other. Therefore, the same applies to the two shaft parts 10 and 32 in the range of their respective end portions, namely the trunnion-shaped end portion 11 of the control shaft 10 and the sleeve-shaped end portion 42 of the auxiliary shaft 32 .
  • the longitudinal toothing 36 of the auxiliary shaft 32 is provided with a bridgework region 58 in which a plurality of teeth 60 of the longitudinal toothing 36 appear to be fused together from tip to tip when viewed in cross-section, this longitudinal toothing 36 thus being, in said region, so to speak provided with a filling.
  • the longitudinal toothing 12 of the control shaft 10 is provided with a teeth gap region 59 in which a plurality of teeth 61 of the longitudinal toothing 12 have been omitted from root to root when viewed in cross-section, this longitudinal toothing thus being provided, in said region, with a recess.
  • the two longitudinal toothing items 12 and 36 only fit each other in such relative rotational positions in which the bridgework region 58 or filling can be introduced into the teeth gap region 59 or recess.
  • An acceptable range of relative rotational positions of the shaft parts 10 and 32 is created by the fact that the bridgework region 58 extends across a smaller number of teeth i.e. with respect to the rotation axis 8 , across a circular arc of smaller extent than the teeth gap region 59 , so that the bridgework region 58 can be introduced into the teeth gap region 59 in a predetermined plurality of acceptable rotational positions.
  • the teeth gap region 59 could be constructed at the shaft part 32 and the bridgework region 58 at the shaft part 10 .
  • each of them would have 28 teeth each extending over a circular arc of about 13 angular degrees.
  • the bridgework region 58 at the shaft part 32 comprises two teeth (about 26 angular degrees) and the teeth gap region 59 at the shaft part 10 comprises six teeth (about 78 angular degrees).
  • the cam disk 14 is formed at the control shaft 10 as an eccentric cylinder offset by about 40% of its radius.
  • the end position of the actuation lever 16 shown in FIG. 3 corresponds to a rotational position of the control shaft 10 in which the cam gear 13 is positioned fully outwards and the cam disk 14 applies the strongest spring-load to the telescopic tappet 15 in the latter's direction of extension.
  • the whole arrangement is dimensioned in such manner that this rotational position provides for proper operating conditions when the thinnest plastic strips available in the provided assortment are being used, for instance with a thickness of 0.4mm.
  • the end position of the actuation lever 16 shown in FIG. 14 corresponds to a rotational position of the control shaft 10 in which the cam gear 13 is positioned about 64 angular degrees, or about 18% of one full revolution, in advance of the rotational position shown in FIG. 3 .
  • this rotational position results in the cam disk 14 being retracted by about 25% of its radius and the telescopic tappet 15 being correspondingly less spring-loaded in its direction of extension.
  • the whole arrangement is dimensioned in such manner that this rotational position provides for proper operating conditions when the thickest plastic strips available in the provided assortment are being used, for instance with a thickness of 1.05 mm.
  • FIG. 13 the dimensions that can be perceived in the illustrated exemplary embodiment (FIG. 13 ) only serve the purpose of illustration and may be selected different, as desired.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Basic Packing Technique (AREA)
  • Lining Or Joining Of Plastics Or The Like (AREA)
  • Orthopedics, Nursing, And Contraception (AREA)
  • Surgical Instruments (AREA)
US09/463,288 1997-07-23 1998-06-18 Hoop-casing device Expired - Fee Related US6463847B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
CH178097 1997-07-23
CH1780/97 1997-07-23
PCT/CH1998/000245 WO1999005025A1 (de) 1997-07-23 1998-06-08 Umreifungsgerät

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US (1) US6463847B1 (de)
EP (1) EP0998409B1 (de)
AT (1) ATE215464T1 (de)
CA (1) CA2297978A1 (de)
DE (1) DE59803636D1 (de)
ES (1) ES2175710T3 (de)
WO (1) WO1999005025A1 (de)

Cited By (6)

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US6564701B1 (en) * 2002-01-28 2003-05-20 Tekpak Corporation Band-thickness adjusting device for a portable packing machine
US20060107624A1 (en) * 2004-11-24 2006-05-25 Hsiu-Man Yu Chen Strap pressing device for a strap packing apparatus
US20070277625A1 (en) * 2004-02-18 2007-12-06 Curtiss Wright Controls, Inc. Linkage and sensor assembly
US7331165B1 (en) * 2006-11-01 2008-02-19 Hsiu-Man Yu Chen Packing machine with an adjustable band-compressing stroke
WO2022052148A1 (zh) * 2020-09-09 2022-03-17 大连富地重工机械制造有限公司 塑料带焊接勾板打扣机
TWI784414B (zh) * 2020-04-09 2022-11-21 大陸商台州市永派包裝設備有限公司 熔接裝置

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DE102009041608A1 (de) * 2009-09-17 2011-04-07 Fromm Holding Ag Umreifungsgerät für ein thermoverschweißbares Kunststoffband

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US4502911A (en) * 1983-07-27 1985-03-05 Cyklop International Emil Hoffman, Kg Strapping machine
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FR2616124A1 (fr) 1987-06-04 1988-12-09 Strapack Corp Appareillage de serrage de bande d'une machine a sangler
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EP0022615A1 (de) 1979-06-04 1981-01-21 Interlake, Inc. Heissiegel-Vorrichtung für eine Umschnürungs-Maschine, Wärmekontroll- und Filterausrüstung zur Verwendung in einer solchen Maschine
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US5954899A (en) * 1998-04-03 1999-09-21 Illinois Tool Works Inc. Strap welding tool with base plate for reducing strap column strength and method therefor

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6564701B1 (en) * 2002-01-28 2003-05-20 Tekpak Corporation Band-thickness adjusting device for a portable packing machine
US20070277625A1 (en) * 2004-02-18 2007-12-06 Curtiss Wright Controls, Inc. Linkage and sensor assembly
US7430927B2 (en) * 2004-02-18 2008-10-07 Curtiss Wright Controls, Inc. Linkage and sensor assembly
US20060107624A1 (en) * 2004-11-24 2006-05-25 Hsiu-Man Yu Chen Strap pressing device for a strap packing apparatus
US7100499B2 (en) * 2004-11-24 2006-09-05 Hsiu-Man Yu Chen Strap pressing device for a strap packing apparatus
US7331165B1 (en) * 2006-11-01 2008-02-19 Hsiu-Man Yu Chen Packing machine with an adjustable band-compressing stroke
TWI784414B (zh) * 2020-04-09 2022-11-21 大陸商台州市永派包裝設備有限公司 熔接裝置
WO2022052148A1 (zh) * 2020-09-09 2022-03-17 大连富地重工机械制造有限公司 塑料带焊接勾板打扣机

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EP0998409B1 (de) 2002-04-03
CA2297978A1 (en) 1999-02-04
DE59803636D1 (de) 2002-05-08
WO1999005025A1 (de) 1999-02-04
EP0998409A1 (de) 2000-05-10
ES2175710T3 (es) 2002-11-16
ATE215464T1 (de) 2002-04-15

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